Impacting machine



Dec. 17, 1968 YF.IM. FROHNAUER, JR

IMPACTING MACHINE 4 Sheets-Sheet l Filed Oct. 19, 1965 J h gt INV:ENTOR.

F. M. FROHNAUER. JR 3,416,418

TMPAGTING MACHINE Dec. 17, 1968 4 Sheets-Sheet 2 Filed Oct. 19, 1965 Dec. 17, 1968 F. M. FROHNAUER. JR 5, 8

IMPACTING MACH INE Filed Oct. 19, 1965 4 Sheets-Sheet 5 v Y w A? Dec. 17, 1968 FROHNAUER' JR 3,416 41 I IMPA-C'IIN'G' MACHINE,

Filed Oct. 19, 1965 4'Sheets Sheet 4 i g Q80 2. g 76 oe as 2 g 78 8e :06; g E g 70 1 iii iii W w 1- M I; ;|i I |:l

FIG. 8 "INVENTOR FRANKLIN M. FRQHNAUER JR United States Patent 01 Rice 3,416,418 Patented Dec. 17, 1968 3,416,418 IMPACTING MACHINE Franklin M. Frohnauer, Jr., Columbus, Ohio, assignor to The Dyna-Quip, Inc., a corporation of Ohio Filed Oct. 19, 1965, Ser. No. 497,638 6 Claims. (Cl. 94-49) ABSTRACT OF THE DISCLOSURE This invention is a machine for imparting impact upon a compressible material utilizing a combustion engine in a structural arrangement with the impact elements wherein the impact action is freely slidably within a cylinder without mechanically engaged guides. Further, the gasolene tank for the engine has been centrally integrated in the over-all structure.

Background Impact machines of the prior art generally comprise an engine supported on a mount, a handle also positioned on the mount, an impact shoe, a rigid housing connecting the engine drive elements to the shoe to impart action to the shoe. Alternatively, the shoe may be reciprocal with the engine to impart reciprocating strokes to the shoe. In either instance, the machines usually incorporate springs in one manner or another. The primary purpose of the springs being to cushion or dampen the shock developed on the down stroke of the impact means. Further, the springs are intended to hold the shoe carrying unit in a neutral position and to return it thereto. Usually the entire shoe carrying unit or the action means to the shoe is slidably mounted with the rigid housing for vertical reciprocating movement.

Further, in the prior art, impacting machines utilizing an internal combustion engine, the fuel tank is positioned on the guide handle, or in an upper region of the engine mount. With this arrangement, the attaching means for the fuel tank are subjected continuously to the impact vibrations of the machine. The inertial of the fuel in the tank causes the attaching means for the tank to be strained and break off after short operation of the machine. Further, the fuel line from the tank to the engine is easily disrupted causing fuel to be lost and as well as malfunction of the engine. In both instances the highly combustible fuel has been a fire hazard to the operatorof additional danger, the upright structure hand mount is relatively close to the operators body and face.

Again, the prior art devices having a direct impact means with a spring return and an upwardly mounted gas tank, have proved to be top heavy and very unwieldly. Also in operation, due to their unbalance, they are very difficult to control and manage.

In the copending application, now Patent No. 3,308,- 728, there is disclosed a tamping machine with an upright configuration. The action impacting means enclosed in the rigid housing is slidably mounted for reciprocating movement by means of an enclosed guide structure. It has now been found that the guide structures do Wear and consequently tend to bind. Also in said co-pending application, the gas tank is mounted on the handle. Here again the tank has become disengaged, caused failure, and created a fire hazard.

Brief description of the invention The present invention overcomes the above-noted disadvantages of the prior art devices as well as that shown in my copending application by providing a unit welded construction having maximum balance that requires only minimum handle pressure when in operation. The number of moving parts and parts in mechanical contact have been reduced drastically.

More specifically, the invention comprises an impact action means freely slidable within a cylinder with no mechanical guide means therebetween. Further, no direct contact is made between the action means and the impacting shoe. This has been achieved without the use of springs, dampers, clutches and gears.

In this way there is no vibrational return to the machine permitting balance and virtually no fatigue to the operator. The shoe is ribbed in addition to having an upright forward section thereby giving a forward direction to the impactor. And, again, adding to the over-all balance.

. Ofreal significance to the unit welded construction is the gas tank mounted on the handle has been eliminated. The gas tank in the present invention has been truly integrated with the over-all welding housing. Of further significance, the gas tank is below the engine and supports the engine. With a Welded housing gas tank below the engine there can be no failure of mounts or fuel lines thereby eliminating engine failure and the fire hazard. But again, by eliminating the weight of the fuel from the support handles and placing the weight of the fuel closer to the center of gravity, the balance of the machine is greatly improved.

Objects It is accordingly a principal object of the present invention to provide an impact machine of unit construction, of nearly perfact balance, and with a considerable reduction in operator fatigue.

Another object of the present invention is to provide an impact machine with a drastic reduction in moving parts in mechanical contact.

Another object of the present invention is to provide an impact machine Where there is no direct contact between a driving element and the impact shoe.

Another object of the present invention is to provide an impact machine utilizing an action means without mechanical guide means.

Still another object of the present invention is to provide an impact machine that does not utilize springs clutches, dampers, or gears.

Further objects and features of the present invention will become apparent from the following detailed descfiiption when taken in conjunction with the drawings in w ich:

Brief description of the drawings FIGURE 1 is a perspective view of the preferred embodiment of an impact machine constructed in accordance with the present invention;

FIGURE 2 is an enlarged partial perspective view, partially in section, of the lower frame portion of the machine of the present invention;

FIGURE 2a is a view looking down on top of FIG- URE 2;

FIGURE 3 is an underside perspective view illustrating the impact shoe of FIGURE 1;

FIGURE 4 is a top-side perspective view illustrating the impact shoe of FIGURE 1;

FIGURE 5 is a sectional view of the weight connecting means;

FIGURES 6, 6a and 6b are a front view, side view and rear view of the gas tank housing incorporated in the preferred embodiment;

FIGURE 7 is a side view of the handle together with the pivot means of the preferred embodiment of FIG- URE 1; and,

FIG. 8 is a side-sectional view illustrating a weight driving means, incorporated in the machine of the present invention.

Detailed description of the drawings Referring now particularly to the preferred embodiment illustrated in perspective in FIGURE 1, the integrated structure of the invention generally comprises a crankshaft housing and gas tank 10, supporting an internal combustion engine 15, and having mounted on its back side the belt driving means housing 20. Fixedly positioned to the housing 20 in an upright manner is the cross-type handle 25. Centrally positioned in the underneath side of the housing 10 is the lower cylinder 30, having permanently mounted on its opposite and lower end the impact shoe 35.

As indicated above, the unit is of unitary construction; that is, the gas tank housing 10, cylinder 30, housing 20, and shoe 35 are each made (in the preferred embodiment) from cast aluminum. The individual components are then bolted or welded together. The tank 10 being formed into a housing by welded seams. The aluminum detracts from the over-all weight but yet is sufficiently thick (in order of A") to provide rigidity.

It is to be noted that the handle 25 neither carries the gasoline tank nor the engine and is free from weight. This, together with placing the weight of the gasoline, i.e., tank, at the center of gravity of the over-all structure makes the unit especially well balanced.

In a quiescent condition, the over-all unit supports itself and is not unwieldly. In operation, the over-all unit may readily be guided and directed by only a slight guidance of the handle by the operator. The unit is relatively quiet and does not have vibrational forces other than that directed to the impact shoe.

As shown in FIGURE 1 the lowermost end of cylinder 30 is terminated in a weld to the mounting plate 32. This plate is, in turn, secured by means of bolts 34a n to a surface plate 36 integrally formed with the shoe 35 (shown in FIGURE 4).

Referring now specifically to the structural details of the various elements and components, reference is had to FIGURES 2 through 7. FIGURES 2 and 2a illustrate the lower part of the cylinder 30, partially cut away to show the counterweight 40 (action means).

The shoe 35 shown in its underside position in FIG- URE 3 and upperside position in FIGURE 4 is made up from the base 37. To provide rigidity ribs 38a 38h are integrally formed on the upper side in its longitudinal direction. Also to provide rigidity, a reinforced wearing surface, and especially directivity means, ribs 39a 39n are formed in the longitudinal axis on the underside of the shoe -35.

Referring back again to FIGURE 2 the counterweight 40 is shown in its lowermost stroke position. In this position it is to be noted that the underside of the counterweight 40 is not in contact with the shoe. There is no physical contact of the counterweight 40 for impaction. Impact of the shoe to the workpiece is caused simply by the gravitational dropping of the weight 40 in the cylinder 30. The outside diameter of the cylindrical weight 40 is somewhat less than the inside diameter of cylinder 30. A film of oil between the cylinder 30 and counterweight 40 provides a slip-fit arrangement; there is no guide means per se.

With continued reference to FIGURES 2 and 5 wherein the upper portion of the counterweight 40, an elongated slot 41 is formed; the depth of the slot extends approximately to the center region of the counterweight 40. At this point, slightly above the lowermost part of the slot, a crossdirectional aperture 43 is bored. Positioned within the slot 41 is a connecting rod 45 having an eyelet 46 at its lowermost portion. The lowermost eyelet retains about 45 rotational freedom when aligned with the aperture 43. A bolt 44 fitted through the aperture 43 and the eyelet 46 on the connecting rod 45 secures the vertical movement of the rod 45 with respect to the cylinder 40.

Referring again to FIGURE 1 and FIGURES 6, 6a, and 6b, at the uppermost end of cylinder 30 there is formed therewith a flange 33 having a series of apertures 31a 31m formed therein. These apertures are in registry with a similar number of apertures 11a 11n formed in the bottom side 12 of the crankshaft housinggas tank 10. An upperside in the form of a plate 13 of the housing 10 supports the engine 15 and carburator 16. The side walls of housing 10 are formed integrally with the back section of the crankshaft housing 20 to complete the structure of the gas tank. A communication 17 extending in fluid tight engagement through the gas tank permits linkage between the belt drive and the counterweight connecting rod 45. The communication 17 is a tube having its one end welded to the front wall of the housing 10 and extends into the crankshaft housing, as explained hereinafter.

The belt driving means for driving the reciprocating weight is fully disclosed in the aforementioned patent; however, for purposes of fully understanding the present invention, reference is made to FIGURE 8. The weight driving means is indicated generally at 70 and enclosed in the previously mentioned drive housing 70. The driving means, a motor pulley 74 is keyed to crankshaft 72 of engine 15 (not shown). A driven pulley 76 is mounted on idler shaft 78 and connected to motor pulley -74 by a belt 80. The weight actuating drive shaft 82 carries a large driven pulley 84 that is connected to a drive pulley 86 on idler shaft 78 by a pair of belts '88. As seen in FIGURE 8 weight crankshaft 82 includes a. crank portion 90, said shaft being journaled in bearings 92.

Also described in said copending application is a novel belt tightening means. With continued reference to FIG- URE 8 the idler shaft 78 is carried on an idler shaft mounting assembly indicated generally at 106. This assembly comprises a mounting flange 108 that is bolted to frame plate 66 by a plurality of studs that extend freely through holes in frame plate 66 and into threaded engagement with holes 112 in mounting flanges 108.

In FIGURE 5 there is shown in detail cross-section in continuation of FIGURE 8-the crank arrangement for providing the action by the reciprocating weight 40. The drive shaft 82 is connected through bearings 92 to crank 90. A crank pin 94 is carried by the crank 90. The connecting rod 45 has its upper eyelet 46 secured by bolt 47 to the crank pin 94. The lower eyelet 44 and bottom portion of connecting rod 45 is pivotly secured within the slot 41 of the weight 40. The rod 45 extends to a general midportion of the weight 40.

The structure of the centrally positioned gas tank is shown in detail in FIGURES 6, 6a, and 6b. Basically, the tank is a cast aluminum box structure 10 having a passage tube 17 centrally positioned. The tube 17 is horizontally aligned with the crankshaft 82 to permit passage therethrough from the pulley arrangement to the crankshaft 90. More specifically, the housing 10 has as its back plate the panel 101 serving also as a back plate for the pulley arrangement. Centrally positioned with respect to the housing 10 is a tube structure 103 passing through the plate 101 and engaging the communication tube 17. The port 104 permits the adjustment means for the pulleys to 'be accessible external of the over-all structure as described in the aforesaid application. The fixed tube 112 permits communication between the gasoline in the tank and the engine, i.e., for the attachment of the carburator 16. The weight of the gasoline is centrally located with respect to the over-all structure and enclosed in a safe and rigid structure-especially away from the handle.

The handle of the present invention is shown removed from the housing and in somewhat more detail in FIG- URE 7. The handle 25 is intended to be rigidly mounted to the basic structure to thereby permit back-and-forth and side-to-side motion by the operator. On the other hand, the handle 25 is designed to ride with the up-and-down vibrational movement of the impactor. More particularly, the vertical inverted U-member is permanently secured to the mounting plate 122 and 122a which in turn is secured to the pulley housing 101. Mounting plates 122 and 1220! having apertures formed therein provide the means for securing. In a generally cross-direction to the vertical member 120 is another U-member 130 positioned horizontally with respect to member 120. The ends of member 130 are welded at 135 and 135a to an upper port of member 120. The two U-members 120 and 130 have the same cross dimension.

On the opposite side of member 130 is another U-mem- =ber 140. This member 140 is also arranged with members 120 and 130 to form a cross. However, member 140 is not rigidly fixed to member 120 as is 130. Member 140 is pivotally mounted to member 120. Pivot rings 141 and 141a fixed to the ends of the U-member 140 are loosely bolted to the plates 143 and 143a respectively. It can be seen from this arrangement that members 120 and 130 form rigid means for two-directional movement and member 140 permits free up-and-down movement.

What is claimed is:

1. A machine for impacting compressible material comprising a cylindrical upright tubular structure,

(a) an impact shoe fixedly positioned at the lowermost end of said cylindrical structure and adapted to maintain said structure in an upright position,

(b) a housing fixedly mounted on the uppermost end of said cylindrical structure,

(0) drive means positioned on an upper region of said housing,

((1) noncontacting weight means in free up-and-down movement in said cylindrical structure,

(e) linkage means connecting said weight to said drive means to cause said weight to nonrestrictively move up and down in said cylindrical structure from a first position adjacent said housing to a second position adjacent to said shoe, and

(f) handle means for directing the movement of said machine, and

(g) said housing includes a front closed section, a central storage area, and a rear closed section, and wherein said linkage means to said drive means is in said rear section, said linkages connecting said weight is in the front section, and wherein said passage is through said central storage section.

2. A machine for impacting compressible material com.-

prising a cylindrical upright tubular structure,

(a) an impact shoe fixedly positioned at the lowermost end of said cylindrical structure and adapted to maintain said structure in an upright position,

(b) a housing fixedly mounted on the uppermost end of said cylindrical structure,

(c) drive means positioned on an upper region of said housing,

((1) noncontacting weight means in free up-and-down movement in said cylindrical structure,

(e) linkage means connecting said weight to said drive means to cause said weight to non-restrictively move up and down in said cylindrical structure from a first position adjacent said housing to a second position adjacent to said shoe,

(f) handle means for directing the movement of Said machine, and

(g) said weight comprises a solid cylindrical mass, a bore located from the uppermost end to a midsection of said weight, said linkage means extending into said bore, and means for securing the end of said linkage means at the lowermost end of said bore.

3. A machine for impacting compressible material comprising a cylindrical upright tubular structure,

(a) an impact shoe fixedly positioned at the lowermost end of said cylindrical structure and adapted to maintain said structure in an upright position,

(b) a housing fixedly mounted on the uppermost end of said cylindrical structure,

(0) drive means positioned on an upper region of said housing,

(d) noncontacting weight means in free up-and-down movement in said cylindrical structure,

(e) linkage means connecting said weight to said drive means to cause said weight to nonrestrictively move up and down in said cylindrical structure from a first position adjacent said housing to a second position adjacent to said shoe,

(f) handle means for directing the movement of said machine,

(g) said impact shoe comprises a substantially squareshaped flat plate structure including an upturned forward section, said upturned forward section of said impact shoe further includes ribs integrally formed in the bottom thereof to impart directivity.

4. An impact machine as set forth in claim 1 wherein said drive means is a gasoline engine and said central storage area is the gasoline storage area for said engine.

5. An impact machine as set forth in claim 2 wherein said bore is elongated in a cross-section direction and wherein said securing means is pivotable.

6. An impact machine as set forth in claim 2 wherein said linkage means and said securing means has an overall extended length that is less than the length of said cylindrical structure thereby preventing contact of said weight with said shoe.

References Cited UNITED STATES PATENTS 2,677,355 5/1954 Maurer 9449 X 2,845,050 7/1958 Wacker 9449 X 3,109,354 11/1963 Van Kirk 9449 3,162,102 12/1964 Juneau 9449 3,232,188 2/1966 Frohnauer 9448 3,236,164 2/ 1966 Miller 9449 3,277,801 10/ 1966 Horvath 9449 3,286,790 11/1966 Kestel 9449 X 3,308,728 3/1967 Brown 94-48 NILE C. BYERS, JR., Primary Examiner. 

